US10288114B2

US10288114B2 - Tapered roller bearing

Info

Publication number: US10288114B2
Application number: US15/542,181
Authority: US
Inventors: Takashi Kawai
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 2015-01-28
Filing date: 2016-01-05
Publication date: 2019-05-14
Anticipated expiration: 2036-01-05
Also published as: CN107110204A; US20180258985A1; US10619668B2; JP2016145637A; US20190203762A1; JP6798780B2; MX2017009747A; EP3252326A1; EP3252326A4; CN107110204B; EP3252326B1

Abstract

A raceway surface (3a) of an outer ring (3) of a tapered roller bearing (1) includes a composite crowning surface. The composite crowning surface includes a center curve (3a1), which is formed at a center portion in a generating-line direction, and end portion curves (3a2 and 3a3), which are formed on both sides of the center curve (3a1) in the generating-line direction. The raceway surface (3a) of the outer ring (3) is entirely subjected to superfinishing. Each of a ratio (R2/R1) of a curvature radius (R2) of the end portion curve (3a2) to a curvature radius (R1) of the center curve (3a1) and a ratio (R3/R1) of a curvature radius (R3) of the end portion curve (3a3) to the curvature radius (R1) is set to 0.02 or more. Each of drop amounts of the end portion curves (3a2 and 3a3) is set to 0.07 mm or less.

Description

The present application is a U.S. National Stage Application of International (PCT) Application No. PCT/JP2016/050147, filed on Jan. 5, 2016, which claims priority to Japanese Patent Application No. 2015-014201, filed on Jan. 28, 2015, and Japanese Patent Application No. 2015-219472, filed on Nov. 9, 2015.

TECHNICAL FIELD

The present invention relates to a tapered roller bearing.

BACKGROUND ART

Reduction in size of a transmission unit or a differential unit (hereinafter referred to as “transmission unit or the like”) of an automobile has been demanded for the purpose of reducing fuel consumption and increasing a cabin space. Along with such demands, reduction in torque and reduction in size have been demanded also for a tapered roller bearing which is to be assembled in the transmission unit or the like. In order to achieve the reduction in torque and reduction in size of the tapered roller bearing, increase in load capacity has been demanded. For example, in Patent Literature 1, there is described a tapered roller bearing having a roller coefficient (roller filling ratio) which is set to more than 0.94 to improve the load capacity.

In recent years, there has been an increasing demand for reduction in size of the transmission unit or the like, and further increase in load capacity has been demanded also for a bearing which is to be assembled in the transmission unit or the like. Further, for the purpose of reducing the size of the transmission unit or the like, employment of an aluminum housing and reduction in thickness of a housing have been considered. In this case, the stiffness of the entire unit is reduced, and a large moment load is applied to the tapered roller bearing. Consequently, a load condition of the tapered roller bearing becomes stricter. Further, when the aluminum housing is employed, the amount of thermal expansion of the housing is increased, with the result that reduction in preload (which is so-called “preload loss”) becomes more liable to occur in the tapered roller bearing. Therefore, more highly functional tapered roller bearing is demanded.

As described above, the demands on the tapered roller bearing have become stricter, and there is difficulty in meeting the demands by only increasing the roller coefficient as in Patent Literature 1.

As a method for further increasing the load capacity of the tapered roller bearing, for example, there has been known a method involving forming each of raceway surfaces of an inner ring and an outer ring into a crowning shape. For example, in Patent Literature 2, there is described a raceway surface including a so-called composite crowning surface. In the composite crowning surface, an arcuate curve having a large curvature radius (large-arc portion) is formed at a center portion of the raceway surface in a generating-line direction, and arcuate curves each having a small curvature radius (small-arc portions) are formed at both end portions of the raceway surface in the generating-line direction. As described above, with the raceway surface including the composite crowning surface, when the large-arc portion formed at the center of the raceway surface and the roller are brought into contact with each other during the normal use, a contact length between the raceway surface and the roller is increased to reduce a surface pressure, thereby being capable of preventing defects such as surface-originating separation in an early stage. Meanwhile, with the small-arc portions formed at the end portions of the raceway surface, the end portions can be recessed toward the side apart from the roller. Therefore, for example, even when a high load is applied to the tapered roller bearing, the contact between the raceway surface of the outer ring and the end portions of the tapered roller is avoided as much as possible, thereby being capable of preventing generation of an excessive edge load.

CITATION LIST

Patent Literature 1: JP 2005-188738

Patent Literature 2: JP 2007-260829

SUMMARY OF INVENTION Technical Problem

Incidentally, in the tapered roller bearing, a contact surface pressure between the raceway surface of the inner ring and the rolling surface of the roller is typically higher than a contact surface pressure between the raceway surface of the outer ring and the rolling surface of the roller. Therefore, the above-mentioned raceway surface including the composite crowning surface has often been applied to the raceway surface of the inner ring which involves a strict load condition, but actually has almost never been applied to the raceway surface of the outer ring which involves a relatively moderate load condition.

In order to meet the demands in recent years for further increase in load capacity in the tapered roller bearing as described above, the inventor of the present invention has conducted an investigation on application of the composite crowning surface not only to the raceway surface of the inner ring but also to the raceway surface of the outer ring. As a result of the investigation, the following problem has been found. In order to avoid the excessive edge load caused by the contact between the raceway surface of the outer ring and the end portion of the tapered roller, it has been considered preferable that the curvature radius of each of the small-arc portions formed at the end portions of the raceway surface of the outer ring be set as small as possible, that is, the curvature be set as large as possible to cause the small-arc portions to be separated from the rolling surface of the tapered roller as much as possible. However, according to the investigation conducted by the inventor of the present invention, it has been found that, when the curvature of each of the small-arc portions at the end portions of the raceway surface is set excessively large, the cycle time for superfinishing applied to the raceway surface becomes longer, thereby leading to a problem of significant degradation in productivity.

The present invention has an object to improve productivity of a tapered roller bearing in which a composite crowning surface is applied to a raceway surface of an outer ring.

Solution to Problem

The raceway surfaces of the outer ring and an inner ring are typically subjected to the superfinishing after grinding. The superfinishing is performed, for example, in the manner as described in Patent Literature 2. That is, under a state in which a grinding wheel is pressed against the raceway surface of the outer ring or the inner ring being rotated, the grinding wheel is reciprocated along a generating-line direction of the raceway surface (see FIG. 7). The inventor of the present invention performed the above-mentioned superfinishing on the raceway surface of the outer ring which is formed of the composite crowning surface. As a result, it has been found that the cycle time becomes longer as a curvature of each of end portion curves of the raceway surface is larger. The following cause is conceivable.

During the superfinishing, while the grinding wheel machines the raceway surface, the grinding wheel itself is also deformed or worn to conform to the raceway surface. As a result, a favorable contact state between the grinding wheel and the raceway surface is obtained, and a machining efficiency is improved. That is, a large-arc portion formed at the center portion of the raceway surface is polished, with the result that the grinding wheel is worn to conform to the large-arc portion. Then, small-arc portions at the end portions of the raceway surface are polished with the grinding wheel, with the result that the grinding wheel is worn to conform to each of the small-arc portions. At this time, when there is a large difference in curvature between the large-arc portion and each of the small-arc portions, it takes a long time period to cause the grinding wheel, which is worn to conform to the large-arc portion, to conform to each of the small-arc portions, with the result that the machining efficiency during this time period is degraded. Similarly, it also takes a long time period to cause the grinding wheel, which is worn to conform to each of the small-arc portions, to conform to the large-arc portion, with the result that the machining efficiency is further degraded.

Based on the findings described above, according to one embodiment of the present invention, there is provided a tapered roller bearing, comprising: an inner ring comprising a raceway surface having a tapered shape on an outer peripheral surface of the inner ring; an outer ring comprising a raceway surface having a tapered shape on an inner peripheral surface of the outer ring; a plurality of tapered rollers, which are arranged between the raceway surface of the inner ring and the raceway surface of the outer ring so as to be rollable and each comprise a rolling surface having a tapered shape on an outer peripheral surface of each of the plurality of tapered rollers; and a cage which is configured to retain the plurality of tapered rollers at predetermined intervals, wherein the raceway surface of the outer ring comprises a composite crowning surface, the composite crowning surface comprising a center curve, which is formed at a center portion in a generating-line direction and has a curvature radius R₁, and end portion curves, which are formed on both sides of the center curve in the generating-line direction and each have a curvature radius R₂,R₃which is smaller than a curvature radius R₁of the center curve, wherein the raceway surface of the outer ring is entirely subjected to superfinishing, and wherein each of a ratio R₂/R₁of the curvature radius R₂of the end portion curve to the curvature radius R₁of the center curve and a ratio R₃/R₁of the curvature radius R₃of the end portion curve to the curvature radius R₁of the center curve is set to 0.02 or more, and each of drop amounts of the end portion curves is set to 0.07 mm or less.

The center curve and the end portion curves are not limited to the arcuate curves, and may comprise non-arcuate curves (for example, logarithmic curves). In the case of the non-arcuate curves, the minimum curvature radii of the non-arcuate curves are set to curvature radii R₁, R₂, and R₃.

As described above, in the raceway surface of the outer ring, a difference between the curvature radius R₁of the center curve and each of the curvature radii R₂and R₃of the end portion curves is suppressed within a predetermined range, and each of drop amounts of the end portion curves is set to a predetermined amount or less. As a result, the cycle time for the superfinishing is shortened, and hence the productivity is improved.

It is preferred that, in the above-mentioned tapered roller bearing, each of the drop amounts of both end portions of the raceway surface of the outer ring be set to 0.02 mm or more. With this, the end portions (end portion curves) of the raceway surface of the outer ring can be sufficiently separated apart from the tapered roller. Therefore, the contact between each of the corner portions of the tapered roller and the raceway surface of the outer ring is avoided as much as possible, thereby being capable of reliably preventing generation of the excessive edge load.

Incidentally, when the thermal expansion occurs in the housing to which the outer ring is fixed, the preload having been applied to the tapered roller bearing may be lost, with the result that the outer ring may be moved relative to the tapered roller toward a small-diameter side in an axial direction. In this case, there is a fear in that the rolling surface of the tapered roller overhangs from the raceway surface of the outer ring toward a large-diameter side to cause generation of the excessive edge load. In particular, the aluminum housing may involve a large amount of thermal expansion. Therefore, when the outer ring is fixed to an inner peripheral surface of the aluminum housing, the above-mentioned problem is conspicuous. Also in such a case of occurrence of the thermal expansion, when the preload is increased to prevent occurrence of the preload loss, an excessively large load is applied to the bearing during the normal use, with the result that the lifetime of the bearing is shortened.

In view of the above, it is preferred that a generating-line-direction width of the raceway surface of the outer ring with respect to the roller rolling surface be set so that the rolling surface of the tapered roller (hereinafter also referred to as “roller rolling surface”) is prevented from overhanging from the raceway surface of the outer ring toward the large-diameter side even when occurrence of the preload loss in the tapered roller bearing causes the outer ring to move relative to the tapered roller in the axial direction. Specifically, it is preferred that, under a state in which the inner ring, the outer ring, and the plurality of tapered rollers are arranged at normal positions, a generating-line-direction dimension W₂(see FIG. 1) of a region of the raceway surface of the outer ring on the large-diameter side from the rolling surface of each of the tapered rollers be set in consideration of the amount of relative movement of the outer ring, which is caused by the preload loss. For example, when the generating-line-direction dimension W₂of the above-mentioned region is set to 0.6 mm or more, the overhanging of the roller rolling surface from the outer ring raceway surface can be prevented even when the preload loss is liable to occur, for example, even when the outer ring is fixed to the aluminum housing. The “state in which the inner ring, the outer ring, and the tapered rollers are arranged at normal positions” corresponds to a state in which an appropriate preload in the axial direction is applied to the inner ring and the outer ring.

For example, in the tapered roller bearing configured to mainly receive the load in a radial direction among bearings configured to support a rotary shaft of a transmission which takes a horizontal posture, a downward load is applied to the inner ring. In this case, most of the load is applied to the tapered rollers on the lower half among the plurality of tapered rollers which are arranged at equal intervals in a circumferential direction, whereas the tapered rollers which are arranged near an upper end are brought into a substantially no-load state. At this time, the interval between the raceway surfaces of the inner ring and the outer ring sandwiching the tapered rollers near the upper end where substantially no load is applied is slightly increased, and the tapered rollers may be moved relative to the outer ring by the amount of the slight increase in interval toward the small-diameter side in the axial direction (see the dotted lines in FIG. 6). In such a case, in order to prevent overhanging of the roller rolling surface from the raceway surface of the outer ring toward the small-diameter side, it is necessary that the raceway surface of the outer ring be extended toward the small-diameter side from the rolling surfaces of the tapered rollers arranged at the normal positions (see the solid lines in FIG. 6). At this time, under the state in which the inner ring, the outer ring, and the plurality of tapered rollers are arranged at normal positions, a distance W₃between a small-diameter-side end surface of each of the tapered rollers and a small-flange portion of the inner ring is set small. With this configuration, even when the tapered rollers are moved toward the small-diameter side, the movement of the tapered rollers can be regulated by causing the tapered rollers to be brought into abutment against the small-flange portion of the inner ring, thereby being capable of reducing the generating-line-direction width of the raceway surface of the outer ring. Specifically, it is preferred that the above-mentioned distance W₃be set to 0.4 mm or less.

Incidentally, with regard to the end portion curves of the outer ring raceway surface on the small-diameter side, when the drop amounts are to be reduced without changing the curvature radii, for example, it is conceivable to move an axial position of the small-diameter-side end surface of the outer ring toward the large-diameter side, to thereby reduce the width of the end portion curves. However, the interval of the small-diameter-side end surface of the outer ring and the large-diameter-side end surface of the inner ring in the axial direction is often determined in accordance with a device in which the tapered roller bearing is to be assembled (for example, a transmission or the like). Therefore, a position of the small-diameter-side end surface of the outer ring may not be changed unreasonably. In view of the above, when an axial width W₁(see FIG. 6) of a chamfered portion formed on a small-diameter-side end portion of the inner peripheral surface of the outer ring is set large, for example, set to 0.5 mm or more, the width of the end portion curve can be reduced, thereby being capable of setting the drop amount to be small without moving the position of the small-diameter-side end surface of the outer ring.

Alternatively, also when a cylindrical surface is formed between the chamfered portion, which is formed on the small-diameter-side end portion of the inner peripheral surface of the outer ring, and the raceway surface, similarly to the above, the width of each of the end portion curves can be reduced, thereby being capable of setting the drop amount to be small without moving the position of the small-diameter-side end surface of the outer ring.

Advantageous Effects of Invention

As described above, according to the tapered roller bearing of the present invention, the cycle time for superfinishing of the raceway surface of the outer ring comprising the composite crowning surface is shortened, thereby being capable of improving the productivity.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a sectional view of a tapered roller bearing according to one embodiment of the present invention, which is taken along an axial direction of the tapered roller bearing.

FIG. 2 is a sectional view of the tapered roller bearing, which is taken along a direction orthogonal to the axial direction.

FIG. 3 is a side view for illustrating an outer ring raceway surface of the tapered roller bearing in an exaggerated manner.

FIG. 4 is a sectional view of another example of the tapered roller bearing, which is taken along the axial direction.

FIG. 5 is a sectional view of the tapered roller bearing of FIG. 1, which is taken along the axial direction, for illustrating a state in which the outer ring of the tapered roller bearing of FIG. 1 is moved in the axial direction.

FIG. 6 is an enlarged view of the tapered roller bearing of FIG. 1.

FIG. 7 is a side view for illustrating a state in which the raceway surface of the outer ring is subjected to superfinishing.

DESCRIPTION OF EMBODIMENTS

Now, a tapered roller bearing according to one embodiment of the present invention is described with reference to the drawings.

As illustrated in FIG. 1 and FIG. 2, a tapered roller bearing 1 of this embodiment comprises an inner ring 2, an outer ring 3, a plurality of tapered rollers 4, and a cage 5. The inner ring 2 comprises a raceway surface 2 a having a tapered shape on an outer peripheral surface thereof. The outer ring 3 comprises a raceway surface 3 a having a tapered shape on an inner peripheral surface thereof. The plurality of tapered rollers 4 are arranged between the raceway surface 2 a of the inner ring 2 and the raceway surface 3 a of the outer ring 3 so as to be rollable and each comprise a rolling surface 4 a having a tapered shape on an outer peripheral surface thereof. The cage 5 is configured to retain the tapered rollers 4 at equal intervals in a circumferential direction. The inner ring 2, the outer ring 3, and the tapered rollers 4 are each made of a steel material, such as bearing steel, carburized steel, or stainless steel. The cage 5 is integrally made of metal or resin. In the following description, a small-diameter side (left side in FIG. 1) of the tapered roller 4 in an axial direction (axial direction of the inner ring 2 and the outer ring 3) is referred to as “small-diameter side”, and a large-diameter side (right side in FIG. 1) of the tapered roller 4 in the axial direction is referred to as “large-diameter side”.

The tapered roller bearing 1 is assembled in, for example, a transmission unit or a differential unit of an automobile. Specifically, as illustrated in FIG. 1, an outer peripheral surface 3 b of the outer ring 3 is press-fitted to an inner peripheral surface 10 a of a housing 10, and an inner peripheral surface 2 b of the inner ring 2 is press-fitted to an outer peripheral surface 20 a of a shaft 20. The housing 10 is made of, for example, aluminum. The shaft 20 is made of, for example, chrome-molybdenum steel. A shoulder surface 10 b of the housing 10 and a shoulder surface 20 b of the shaft 20 sandwich and pressurize an end surface 3 c of the outer ring 3 on the small-diameter side and an end surface 2 c of the inner ring 2 on the large-diameter side from both sides in the axial direction, to thereby apply a preload in the axial direction to the tapered roller bearing 1. In the illustrated example, a shim 30 is interposed between the end surface 3 c of the outer ring 3 on the small-diameter side and the shoulder surface 10 b of the housing 10. A thickness of the shim 30 is suitably set so that a magnitude of the preload to be applied to the tapered roller bearing 1 is adjusted.

The inner ring 2 has a small-flange portion 2 d and a large-flange portion 2 e. The small-flange portion 2 d is formed on the small-diameter side of the raceway surface 2 a. The large-flange portion 2 e is formed on the large-diameter side of the raceway surface 2 a. The raceway surface 2 a of the inner ring 2 comprises a crowning surface formed of a single curve, or a composite crowning surface formed of a center curve and end portion curves formed on both sides of the center curve. Each curve is formed of an arc or a logarithmic curve.

As illustrated in FIG. 3, the raceway surface 3 a of the outer ring 3 is formed of a center curve 3 a 1 which is formed at a center portion in a generating-line direction, an end portion curve 3 a 2 on the small-diameter side which is adjacent to the small-diameter side (left side in FIG. 3) of the center curve 3 a 1, and an end portion curve 3 a 3 on the large-diameter side which is adjacent to the large-diameter side (right side in FIG. 3) of the center curve 3 a 1. In this embodiment, the center curve 3 a 1 comprises an arcuate curve having a curvature radius R₁. The end portion curve 3 a 2 on the small-diameter side comprises an arcuate curve having a curvature radius R₂. The end portion curve 3 a 3 on the large-diameter side comprises an arcuate curve having a curvature radius R₃. The center curve 3 a 1 and each of the end portion curves 3 a 2 and 3 a 3 smoothly continue so as to have common tangential lines at borders P₁and P₂. In FIG. 3, curvatures of the curves 3 a 1, 3 a 2, and 3 a 3 of the raceway surface 3 a are illustrated in an exaggerated manner.

In the outer raceway surface 3 a of the outer ring 3, each of a ratio R₂/R₁of the curvature radius R₂of the end portion curve 3 a 2 to the curvature radius R₁of the center curve 3 a 1 and a ratio R₃/R₁of the curvature radius R₃of the end portion curve 3 a 3 to the curvature radius R₁of the center curve 3 a 1 is set to 0.02 or more, preferably 0.04 or more. Further, each of the ratio R₂/R₁and the ratio R₃/R₁is set to 0.3 or less, preferably 0.1 or less. Each of drop amounts D₁and D₂of the end portion curves 3 a 2 and 3 a 3 is set to 0.02 mm or more and 0.07 mm or less. The drop amounts D₁and D₂of the end portion curves 3 a 2 and 3 a 3 are widths of the end portion curves 3 a 2 and 3 a 3 in a direction orthogonal to a generating-line direction of the raceway surface 3 a. Specifically, the generating-line direction of the raceway surface 3 a corresponds to a direction of a straight line connecting ends (borders P₁and P₂) of the center curve 3 a 1.

In this embodiment, an axial width W₁(see FIG. 6) of a chamfered portion 3 d formed on a small-diameter-side end portion of the inner peripheral surface of the outer ring 3 is set large so that an axial width of the end portion curve 3 a 2 on the small-diameter side of the raceway surface 3 a is set small. With this configuration, without changing an axial position of the small-diameter-side end surface 3 c of the outer ring 3, the drop amount D₁of the end portion curve 3 a 2 on the small-diameter side can be set small. The axial width W₁of the chamfered portion 3 d is set to, for example, 0.5 mm or more. Further, in order to secure the drop amount D₁of the end portion curve 3 a 2 on the small-diameter side to be 0.02 mm or more, the axial width W₁of the chamfered portion 3 d is set to, for example, 1.0 mm or less.

Instead of or in addition to setting the axial width W₁of the chamfered portion 3 d to be large, as illustrated in FIG. 4, a cylindrical surface 3 f may be formed between the chamfered portion 3 d and the raceway surface 3 a to suppress the drop amount D₁of the end portion curve 3 a 2 on the small-diameter side.

The rolling surface 4 a of the tapered roller 4 has a substantially linear tapered surface, a crowning surface having a single curve, or a composite crowning surface comprising a center curve and end portion curves formed on both sides of the center curve. At both ends of the outer peripheral surface of the tapered roller 4, there are formed

chamfered portions

4 b and 4 c which are adjacent to the rolling surface 4 b.

In the tapered roller bearing 1 of this embodiment, for example, an inner diameter of the inner ring 2 is set within a range of from 15 mm to 120 mm. An outer diameter of the outer ring 3 is set within a range of from 30 mm to 250 mm. A combination width, which is an axial width between the small-diameter-side end surface 3 c of the outer ring 3 and the large-diameter-side end surface 2 c of the inner ring 2, is set within a range of from 7 mm to 50 mm. Further, in the tapered roller bearing 1 of this embodiment, the tapered rollers 4 are loaded at high density. Specifically, a roller coefficient γ expressed by the following expression is set to γ>0.94.
γ=(Z·DA)/(π·PCD)

In the above-mentioned expression, Z represents the number of rollers, DA represents an average diameter of the rollers, and PCD represents a pitch circle diameter of the rollers.

The cage 5 comprises a small-diameter side annular portion 5 a, a large-diameter-side annular portion 5 b, and a plurality of columnar portions 5 c connecting the small-diameter-side annular portion 5 a and the large-diameter-side annular portion 5 b to each other in the axial direction (see FIG. 1 and FIG. 2). The cage 5 is arranged on a radially outer side of centers of the tapered rollers 4 and at a position of not being held in contact with the outer ring 3. Column surfaces 5 d of the columnar portions 5 c, which are held in contact with the tapered rollers 4, are inclined so that a gap formed between the column surfaces 5 d opposed to each other in the circumferential direction increases as approaching the radially inner side.

The tapered roller bearing 1 allows the inner ring 2 and the outer ring 3 to rotate relative to each other while holding the large-diameter-side end surfaces 4 e of the tapered rollers 4 in slide contact with the large-flange portion 2 e of the inner ring 2. At this time, when preload loss occurs due to some cause, and the outer ring 3 is moved relative to the tapered roller 4 toward the small-diameter side (see FIG. 5), there is a fear in that the rolling surfaces 4 a of the tapered rollers 4 may overhang from the raceway surface 3 a of the outer ring 3 toward the large-diameter side to cause generation of an excessive edge load.

In view of the above, it is preferred that, under a state in which the inner ring 2, the outer ring 3, and the tapered rollers are arranged at normal positions (see FIG. 1), a generating-line-direction dimension W₂of a region of the raceway surface 3 a of the outer ring 3 on the large-diameter side from the rolling surfaces 4 a of the tapered rollers 4, that is, a generating-line direction distance between the large-diameter-side end of the rolling surface 4 a of the tapered roller 4 and the large-diameter-side end of the raceway surface 3 a of the outer ring 3 be set large in consideration of the preload loss. Particularly in the case where the housing 10 is made of aluminum, the housing 10 involves a large amount of thermal expansion, and hence the preload of the tapered roller bearing 1 is liable to be lost. In such a case, it is preferred that the generating-line-direction dimension W₂of the above-mentioned region be set to, for example, 0.6 mm or more.

In this embodiment, a distance W₃(see FIG. 6) between an end surface 4 d of the tapered roller 4 on the small-diameter side and the small-flange portion 2 d of the inner ring 2 is set small in advance. Specifically, under the state in which the inner ring 2, the outer ring 3, and the tapered rollers 4 are arranged at the normal positions, the above-mentioned distance W₃is set to 0.4 mm or less. With this configuration, even when the tapered rollers 4 are moved toward the small-diameter side due to some cause, the tapered rollers 4 are brought into abutment against the small-flange portion 2 d in an early stage (see the dotted lines in FIG. 6). With this configuration, the amount of movement of the tapered rollers 4 toward the small-diameter side can be suppressed. Therefore, without extension of the raceway surface 3 a of the outer ring 3 (in particular, the end portion curve 3 a 2 on the small-diameter side) toward the small-diameter side, overhanging of the roller surfaces 4 a of the tapered rollers 4 from the raceway surface 3 a of the outer ring 3 toward the small-diameter side can be prevented. When the above-mentioned distance W₃is excessively small, oil is less likely to flow in through the gap formed between the end surfaces 4 d of the tapered rollers 4 on the small-diameter side and the small-flange portion 2 d of the inner ring 2. Therefore, it is preferred that the above-mentioned distance W₃be set to 0.2 mm or larger.

The raceway surface 2 a of the inner ring 2, the raceway surface 3 a of the outer ring 3, and the rolling surfaces 4 a of the tapered rollers 4 are subjected to grinding, and thereafter are subjected to superfinishing. The superfinishing on the raceway surface 3 a of the outer ring 3 is performed in the following manner. Under a state in which the outer ring 3 is rotated about a center axis thereof, as illustrated in FIG. 7, a grinding wheel 6 is pressed against the raceway surface 3 a and reciprocated along the generating-line direction of the raceway surface 3 a. At this time, while the grinding wheel 6 is reciprocated along the entire raceway surface 3 a, the grinding wheel 6 may be finely vibrated in the generating-line direction. The grinding wheel 6 is pressed against the center curve 3 a 1 in such a manner. As a result, the distal end surface of the grinding wheel 6 is deformed to conform to the center curve 3 a 1, and the center curve 3 a 1 is polished. Then, the grinding wheel 6 is pressed against the end portion curves 3 a 2 and 3 a 3, with the result that the distal end surface of the grinding wheel 6 is deformed to conform to the end portion curves 3 a 2 and 3 a 3, and the end portion curves 3 a 2 and 3 a 3 are polished.

At this time, as described above, the difference between the curvature radius R₁of the center curve 3 a 1 and each of the curvature radii R₂and R₃of the end portion curves 3 a 2 and 3 a 3 is suppressed to be relatively smaller (R₂/R₁≥0.02 and R₃/R₁≥0.02). Therefore, the amount of deformation of the distal end of the grinding wheel 6 is relatively smaller when the grinding wheel 6 moves from the center curve 3 a 1 to the end portion curves 3 a 2 and 3 a 3 or moves from the end portion curves 3 a 2 and 3 a 3 to the center curve 3 a 1. With this, the grinding wheel 6 conforms to the curves 3 a 1, 3 a 2, and 3 a 3 in an early stage. As a result, machining is performed with high efficiency, and the cycle time for the superfinishing is shortened, thereby improving the productivity of the tapered roller bearing 1.

The present invention is not limited to the above-mentioned embodiment. For example, in the above-mentioned embodiment, description is made of the case where all of the center curve 3 a 1 and the end portion curves 3 a 2 and 3 a 3 of the raceway surface 3 a of the outer ring 3 are arcuate curves. However, the present invention is not limited to this case. Any or all of those curves may be non-arcuate curves (for example, logarithmic curves). For example, the center curve 3 a 1 may be an arcuate curve, and both end portion curves 3 a 2 and 3 a 3 may be logarithmic curves. Further, the curvature radius R₂of the end portion curve 3 a 2 on the small-diameter side and the curvature radius R₃of the end portion curve 3 a 3 on the large-diameter side may be equal to or different from each other.

In order to verify the effect of the present invention, the following test was conducted. First, various types of tapered roller bearings having different design dimensions (in particular, factors of the outer ring raceway surface) were prepared, and were identified as Examples 1 to 8 and Comparative Examples 1 to 5. Each tapered roller bearing had the same configuration as that of the embodiment illustrated in FIG. 1 to FIG. 3, and design dimensions of respective parts are shown in the following Table 1. Research was made on the following Items (1) to (3) for those tapered roller bearings.

	TABLE 1

	Bearing functional
	property

Design dimensions

(1)

(2)

(3)

R₂/R₁

Cycle

Contact

Roller

A

B

L₁

L₂

L₃

R₁

R₂

R₃

R₃/R₁

D₁

D₂

W₁

W₂

W₃

time

pressure

position

Example 1	70	15	9.1	2.6	2.1	3450	100	100	0.029	0.037	0.025	0.5	0.8	0.3	∘	∘	∘
Example 2	75	17	11.2	2.8	2.4	5300	150	150	0.028	0.029	0.022	0.5	0.67	0.31	∘	∘	∘
Example 3	70	23	15.1	4.3	3.1	9500	200	200	0.021	0.050	0.026	0.7	0.7	0.2	∘	∘	∘
Example 4	80	14.8	8.4	3.2	2.5	2200	100	100	0.045	0.057	0.036	0.5	0.9	0.25	∘	∘	∘
Example 5	69	12.5	7.2	2.3	1.8	1300	80	80	0.062	0.039	0.025	0.5	0.9	0.3	∘	∘	∘
Example 6	66	12.4	6.3	2.1	1.7	1000	60	60	0.060	0.043	0.029	0.5	0.8	0.3	∘	∘	∘
Example 7	66	12.4	6.3	2.1	1.7	1700	40	40	0.024	0.059	0.039	1.2	0.45	0.7	∘	∘	x
Example 8	70	15	9.1	2.6	2.1	3450	300	300	0.087	0.015	0.010	1.2	0.5	0.5	∘	x	x
Comparative	70	15	9.1	2.6	2.1	3450	50	50	0.014	0.071	0.047	1.2	0.5	0.5	x	∘	x
Example 1
Comparative	75	17	11.2	2.8	2.4	5300	50	50	0.009	0.081	0.060	1.5	0.3	0.6	x	x	x
Example 2
Comparative	70	23	15.1	4.3	3.1	14300	80	80	0.006	0.118	0.062	1	0.5	0.6	x	∘	x
Example 3
Comparative	80	14.8	8.4	3.2	2.5	4400	40	40	0.009	0.131	0.081	1.2	0.45	0.5	x	x	x
Example 4
Comparative	69	12.5	7.2	2.3	1.8	2200	40	40	0.018	0.070	0.043	1	0.35	0.5	x	x	x
Example 5

A (mm): Outer diameter dimension of the outer ring 3
B (mm): Axial width of the outer ring 3
L₁(mm): Generating-line-direction dimension of the center curve 3a1 of the raceway surface 3a of the outer ring 3
L₂(mm): Generating-line-direction dimension of the end portion curve 3a2 on the small-diameter side of the raceway surface 3a of the outer ring 3
L₃(mm): Generating-line-direction dimension of the end portion curve 3a3 on the large-diameter side of the raceway surface 3a of the outer ring 3
R₁(mm): Curvature radius of the center curve 3a1 of the raceway surface 3a of the outer ring 3
R₂(mm): Curvature radius of the end portion curve 3a2 on the small-diameter side of the raceway surface 3a of the outer ring 3
R₃(mm): Curvature radius of the end portion curve 3a3 on the large-diameter side of the raceway surface 3a of the outer ring 3
D₁(mm): Drop amount of the end portion curve 3a2 on the small-diameter side of the raceway surface 3a of the outer ring 3
D₂(mm): Drop amount of the end portion curve 3a3 on the large-diameter side of the raceway surface 3a of the outer ring 3
W₁(mm): Axial width of the chamfered portion 3d on the small-diameter side of the outer ring 3
W₂(mm): Generating-line-direction dimension of the region of the raceway surface 3a of the outer ring 3 on the large-diameter side from the rolling surface 4a of the tapered roller 4
W₃(mm): Distance between the end surface 4d of the tapered roller 4 on the small-diameter side and the small-flange portion 2d of the inner ring 2

(1) Cycle Time for Superfinishing of Outer Ring Raceway Surface

The raceway surface of the outer ring of each tapered roller bearing was subjected to the superfinishing by the method illustrated in FIG. 7, and the cycle time for the superfinishing was measured. As a determination criterion, the mark of “∘” was given when the cycle time was 30 seconds or less, and the mark of “×” was given when the cycle time exceeded 30 seconds.

(2) Surface Pressure (Edge Stress)

The inner ring was rotated under a state in which a predetermined preload was applied to the inner ring and the outer ring of each tapered roller bearing, and the surface pressure during the rotation was measured. The measurement of the surface pressure was performed by measuring the applied load through residual stress measurement with use of an X-ray. The edge portion at which the end portions of the raceway surfaces of the inner ring and the outer ring and the rollers are held in contact was subjected to the measurement. As a determination criterion, the mark of “∘” was given when the surface pressure was 4,000 MPa or less, and the mark of “×” was given when the surface pressure exceeded 4,000 MPa.

(3) Position of Tapered Roller During Preload Loss

The inner ring was rotated under the state in which the predetermined preload was applied to the inner ring and the outer ring of the tapered roller bearing, and the presence or absence of a linear edge contact mark, which may be formed at the time of overhanging of the roller from the outer ring raceway surface large-diameter side, on the roller rolling surface radially outer side was checked. When the linear edge contact mark was formed on the roller large-diameter-side rolling surface, the mark of “×” was given.

As shown in Table 1, in Examples 1 to 8 in which each of curvature radius ratios R₂/R₁and R₃/R₁of the end portion curves to the center curve of the outer ring raceway surface was set to 0.02 or more and in which each of the drop amounts of the end portion curves was set 0.07 mm or less, the cycle time for the superfinishing of the outer ring raceway surface was 30 seconds or less. In contrast, in Examples 1 to 5 in which each of the curvature radius ratios R₂/R₁and R₃/R₁was less than 0.02 and in which each of the drop amounts of the end portion curves was more than 0.07 mm, the cycle time for the superfinishing of the outer ring raceway surface was longer than 30 seconds. Further, in Examples 4, 5, 6, and 8 in which each of the curvature radius ratios R₂/R₁and R₃/R₁was especially larger, that is, was set to 0.04 or more, the cycle time for the superfinishing was especially shorter.

Further, in Examples 1 to 6, each of the drop amounts of the end portion curves of the outer ring raceway surface was set to 0.02 mm or more. The width W₂in the region of the outer ring raceway surface on the large-diameter side from the tapered roller was set to 0.6 mm or more. The distance W₃between the small-flange portion of the inner ring and the end surface of the tapered roller on the small-diameter side was set to 0.4 mm or less. In Examples 1 to 6, the edge stress was not generated, and there was no abnormality in the surface pressure distribution also during the preload loss. Thus, the tapered roller bearings of Examples 1 to 6 had sufficient durability.

In contrast, in Example 8, each of the drop amounts of the end portion curves of the outer ring raceway surface was less than 0.02 mm. Consequently, the excessive edge stress was generated, and the edge portion was damaged. In Example 7 and Comparative Examples 1 to 5, each of the drop amounts of the end portion curves of the outer ring raceway surface was set to 0.02 mm or more. However, the width W₂of the region of the outer ring raceway surface on the large-diameter side from the tapered roller was less than 0.6 mm, and the distance W₃between the small-flange portion of the inner ring and the end surface of the tapered roller on the small-diameter side exceeded 0.4 mm. Consequently, during the preload loss, the rolling surface of the tapered roller overhung relative to the raceway surface of the outer ring, and the edge of the end portion of the raceway surface was brought into contact with the roller rolling surface. As a result, the edge portion of the roller rolling surface or the raceway surfaces of the inner ring and the outer ring were damaged.

REFERENCE SIGNS LIST

1 tapered roller bearing
2 inner ring
2 a raceway surface
2 d small-flange portion
2 e large-flange portion
3 outer ring
3 a raceway surface
3 a 1 center curve
3 a 2, 3 a 3 end portion curve
3 d, 3 e chamfered portion
4 tapered roller
4 a rolling surface
5 cage
10 housing
20 shaft
30 shim

Claims

The invention claimed is:

1. A tapered roller bearing, comprising:

an inner ring comprising a raceway surface having a tapered shape on an outer peripheral surface of the inner ring;

an outer ring comprising a raceway surface having a tapered shape on an inner peripheral surface of the outer ring;

a plurality of tapered rollers, which are arranged between the raceway surface of the inner ring and the raceway surface of the outer ring so as to be rollable, each of the plurality of tapered rollers comprising an outer peripheral surface having a rolling surface with a tapered shape; and

a cage which is configured to retain the plurality of tapered rollers at predetermined intervals,

wherein the raceway surface of the outer ring comprises a composite crowning surface, the composite crowning surface comprising a center curve, which is formed at a center portion in a generating-line direction and has a curvature radius R₁, and end portion curves, which are formed on both sides of the center curve in the generating-line direction, one of the end portion curves having a curvature radius R₂that is smaller than the curvature radius R₁of the center curve, and another of the end portion curves having a curvature radius R₃that is smaller than the curvature radius R₁of the center curve,

wherein the raceway surface of the outer ring is entirely subjected to superfinishing, and

wherein each of a ratio R₂/R₁of the curvature radius R₂of the one end portion curve to the curvature radius R₁of the center curve and a ratio R₃/R₁of the curvature radius R₃of the other end portion curve to the curvature radius R₁of the center curve is set to 0.02 or more, and each of drop amounts of the end portion curves is set to 0.02 mm or more and 0.07 mm or less.

2. The tapered roller bearing according to claim 1, wherein, under a state in which an appropriate preload in an axial direction is applied to the inner ring and the outer ring, a generating-line-direction dimension of a region of the raceway surface of the outer ring on a large-diameter side from the rolling surfaces of the plurality of tapered rollers is set to 0.6 mm or more.

3. The tapered roller bearing according to claim 1,

wherein the inner ring comprises a small-flange portion which is formed on a small-diameter side of the raceway surface of the inner ring, and

wherein, under a state in which an appropriate preload in an axial direction is applied to the inner ring and the outer ring, a distance between a small-diameter-side end surface of each of the plurality of tapered rollers and the small-flange portion of the inner ring is set to 0.4 mm or less.

4. The tapered roller bearing according to claim 1, wherein the outer ring comprises a chamfered portion formed on a small-diameter-side end portion of the inner peripheral surface of the outer ring, the chamfered portion having an axial width of 0.5 mm or more.

5. The tapered roller bearing according to claim 1, wherein the outer ring comprises a cylindrical surface formed between a chamfered portion, which is formed on a small-diameter-side end portion of the inner peripheral surface of the outer ring, and the raceway surface of the outer ring.